Rotary compressor and pump



.W. P. DALRYMPLE Filed Feb. 17, 1930 ROTARY COMPRESSOR AND PUMP June 28,1932.

June 28, 1932. w. P. DALRYMPLE ROTARY COMPRESSOR AND PUMP Filed Feb. 17,I930 2 Sheets- Sheet 2 ZZZZZZZIanl .P DaZrz-ymple Patented June 28,1932,

UNITED sTATEs PATENT OFFICE- WILLIAM I. DALRYMPLE, OF CHICAGO, ILLINOIS,ASSIGNOR OF ONE-HALF '10 GAMEROfi A. WHI'ISETT, OF CHICAGO, ILINOISROTARY comrnnsson Ann PUMP The present invention "relates to rotarycompressors or pumps forfhandling either gases or liquids, and servingasa compressor or a pump, depending upon the requirements of theparticular use. v

()ne of the principal objects of the invention is to provide an improvedconstruction of rotary pump or the like Characterized by an outercasing, a rotor therein having peripheral working chambers, and arotating liquid ring in said casing serving as the piston for each ofthe rotor working chambers. This liquid ring revolves at approximately 7the same speed as the rotor, and in addition to serving as a piston forthe rotor chambers also functions as a sealing medium for sealing thespace between each side of the rotor and the adjacent side wall of thecasing, thereby enabling therotor to be spaced from the casing, so thatthere is no'metal to-metal contact between rotating and stationary partsat any point in the construction.-

Those lateral portions of the liquid ringrevolving between the outersides of the rotor and the casing, and performing the above scalingfunction, transmit their centrifugal force as an inwardly actingpressure upon the intermediate portion of the liquid ring 7 whichrevolves in the plane of the rotor chambc'rs, and one of the features ofthe invention is the provision of displacement surfaces .or members inthe casing, wherebythe level of these two outer portions can beincreased considerably beyond the level of theintermediate portion atthe compression stage ot the cycle for establishing a relatively largepressure differential between these outer por-' tions of the liquid ringand the intermediate portion thereof. Such enables relatively highpumping or compression pressures to be developed in the device. T

Another important object of the invention is to provideimproved valvemeansfor the working chambers of the rotor. Such valve meansmay be of amechanical type or of a liquid type, both embodiments being shown in thepresent application. In the mechania cal embodiment, one of the featuresof thein vention resides in properly relating centrifugal forces andvalve -move inent; whereby efii Insein'e instances, it may be desira 1eto cool m cient and reliable valve operation is obtained. In the liquidembodiment, the intake to the rotor chambers or the exhaust therefrom,or both, is governed by: the cyclical immersion of intake and outletports inrotating rings of liquid revolving with the rotor.

The liquid type of valve means has the advantage of avoiding theobjection ofim perfectvalve seating, results in a more quiet operation,and is capableof handling fluids which would be diflicult to handle'withthe metallic" valves." In this regard, the present device isparticularly adaptable to use as a refrigerant compressor forrefrigerating ap paratus, by virtue of the fact that there are nopistons or other pumping parts requiring lubrication, nor are there anyother oints which cannot be effectively sealed against leakage of therefrigerant.

Other objects and advantages of the invention will be apparent fromthefollowing detail description of certain preferred enibodiments thereof.In the accompanying drawings illustratingsuch embodiments:

Figure 1 is a vertical transverse sectional view through a relativelysimple form of my invention, utilizing mechanical exhaust valves for therotor chambers, this 'fi ure corresponding to a section taken on the Pam: ofthe line ll of Figure 2; l e p Figure 2 is a vertical axialsectional view of the same, taken approximately on the plane of the line2-2 of Figure 1';

Figures 3, 4 and 5 are vertical axial sec tional ,VlGWSOf otherembodiments.

Referring to Figures 1 and 2, thecasing of the device comprises anintermediate ring or cylindrical portion 321, which is secured to asuitable base 22, as byzthe cap screws 23. The sides ,of thisintermediate ring portion are closed by the side or end walls 25 and 26,which are secured to the cylin-' inner faces-of the end plates 25, 26and the edges of theintermediate 'easin portion.

or other suitable pipe connection extends.

for conveying the refrigerant, air or other fluid being handled, intothe interior of the casing. For brevity of description, I shallhereinafter refer to this fluid, which is being pumped or compressed inthe unit, as the working fluid. Projecting from one of the end plates 25or 26 is a boss 38, with which a nipple or other pipe connection 39communicates for conveying the working fluid from the unit. Formed as apart of the end plate 25 is a bearing boss 41, in which the drive shaft42 is journalled. This bearing is preferably packed by a suitable glandpacking 43 adapted to be taken up by an adjustable packing nut 44 havingthreaded engagement with the bearing boss 41. The drive shaft 42 extendstransversely through the casing and has a reduced portion 42 at itsother end extending into a bearing boss 46 projecting from theother endplate 26. A bearing bushing 47 is adjustably mounted in the boss. 46 forreceiving the reduced shaft end 42. The end of said bearing boss issealed-by a cap nut 48 screwing over the boss and compressing a gasketring 49 against the end of the boss. a

The rotor is designated 52 in its entirety and comprises a hub 53, whichis secured to the drive shaft 42 by a key 54. Interposed between one endof the hub 53 and the bearing boss 41 are washers or bearing rings 55,and engaging with the other end of the hub 53is any suitable means forholding the rotor against displacementalong the shaft, such as the twolock nuts 56 screwing over the threaded portion 42 of the drive shaft. Aplate member 58 is interposed between these nuts and the end of the hub53, such plate member being secured to the drive shaft by the key 54 andcomprising part of a ball valve cage, as I shall presently describe.

The rotor comprises a relatively narrow web portion 61 extendingoutwardly from the hub 53, and a relatively wide body portion 62extending outwardly from this web portion. Projecting outwardly beyondthe periphery of the body portion 62, at each side thereof, are sidewalls or flanges 64. These annular side walls may be in the form ofseparate plates rigidly secured to the body portion 62,-or they may bein the form of integral extensionsof the'body portion. A pluralityofirelatively small vanes or fins 66project outwardly from. these, sideflanges at spaced the periphery of the rotor body portion 62 and extendfrom side to side across the channel area 68, between the inner sides ofthe lateral flange portions 64. These baflles or dividing walls may beformed integrally with the rotor body portion or with the side flanges64, or they may consist of separate plates recessed into the rotor bodyportion and having tight-fitting engagement against the inner sides ofthe flange portions 64. The arcuate spaces between such dividing walls69 constitute working chambers 72, in which the working fluid iscompressed. It will be noted that the dividing walls do not extend outto the peripheral edges of the flanges 64, but have their outer edgesspaced inwardly considerably from the flange peripheries.

This permits a displacement member to be extended into the channel area68, in close proximity to the outer edges of the dividing walls 69 andthe working chambers 7 2 for securing an efficient pumping displacementof the liquid ring, as I shall presently describe.

Extending inwardly from each pumping chamber 72 is an exhaust passageway7 3, which is normally closed at its inner end by a ball valve 74seating in the end of said passageway. These ball valves are disposed inan annular pocket 75 defined within the center of the rotor body portion62, The balls are held against displacement in one direction by the webportion 61 and in the other direction by the plate 58, suchplate servingas a valve cage and having ribs 7 6 extending from the inner sidethereof and serving as spacers between the balls for holding them inproper alignment with their respective discharge passageways 7 3. In theoperation of the. device, the balls are normally held pressed outwardlyagainst theinner ends of the passageways 73 under the action ofcentrifugal force and are unseated from these passageways by thepressure of the fluid being compressed in the working chambers 72. Theworking fluid, after being discharged past these ball valves'enters theinterior of the casing and then passes out through the dishaving theoutwardly acting centrifugal 88 thereof is a displacement member 79 inthe form of a ring .or segment secured to the cylindrical casing portion21. This displacement .member acts on the intermediate or inner leg ofthe liquid ring rotating between the side flanges 64 of the rotor, suchdisplacement member being spaced from the inner sides of the flanges topermit the inward and outward flow of liquid along the sides of saidmember. Also mounted in the casing on opposite sides of the rotor aredisplacement members 81, 81 which act on the outer legs of the liquidring. These lateral displacement members are spaced slightly from theedges of the vanes 66. Referring to Figure 1, it will be seen that theinner surface of the intermediate displacement member 79 is of a maximumradius at the intake point of the rotor cycle and from this pointspirals inwardly through a gradually diminishing radius to the dischargezone of the rotor cycle, at which point such inner surface just clearsthe outer edges of the dividing walls 69. From this zone or point ofsmall radius, the inner surface of the displacement member then extendsoutwardly at the shoulder or offset portion 83, to the larger radius atthe intake zone of the cycle. The working fluid is introduced intotherotor through an inlet port-85 communicating with the fluid inletconnection 36 and opening into't-he channel area of the rotor throughthe offset angle portion 83.

In the operation of the device, as the rotor 'is brought up to speed,the pumping liquid is whirled outwardly under the action of centrifugalforce and assumes approximately the condition or form illustrated inFigures 1 and 2. The revolving liquid ring may be regarded as beingdivided into three main volumes or quantities, at least during thecompression stage of the cycle, consisting of the intermediate volume orleg a" rotating within the channel periphery of the rotor and the twoouter volumes or legs y, 3 rotating on the outer sides of the rotor. Itwill be noted that the intermediate leg 00 has the relation of one legof a U-tube with respect to each outer leg y. That is to say, by

pressures of the two outer legs 3/ preponderate over the outwardlyacting centrifugal pressure of the intermediate leg as, an in- Wardlyacting compression .pressurecan be created between the inner end of theleg 02 and the bottoms of the working chambers '"2. Such preponderating'centrifugal pres sure of the two outer legs may be obtained by makingeach outer leg of greater depth at this point in the cycle so thatcentrifugal force acting on this greater radius of liquid'wi'll tend toforce the intermediate leg 02 to the same balancing radius. Thesedifferential radii or levels of the three legs are attained by thedisplacementmembers in the -.casing.;,

Referring to Figure ,1,'that portion of the casing .at theleft-hand'side of the rotor may be regarded as the intake stage of thecycle, and that portion on the right-hand side of the rotor may beregarded as the compression or exhaust stage of the cycle.

At the intake stage or zone, the inner :surface of the intermediatedisplacement memher 7 9 recedesaway from the rotor so that in this partof the casing, the intermediate liquid leg a is whirled outwardly clearof the dividing walls 69-and working chambers 72. At this intake zone,the two outer displace; ment members 81, 81 also recede outwardly tolower or diminish the height of the two outer liquid legs 3 3/, therebyassisting in permitting the intermediate liquid leg :1: to be whirledout clear of the dividing walls 69. The inlet port 85 opens into thechannel area 68 between the side flanges 64 and the working fluid whichis drawn in through this port bubbles through the intermediate leg w ofthe liquid pumping ring, substantially as indicated in Figure l. Thepumping ringeof liquid will, in all instances, be of higher specificgravity than the fluid being. pumped or compressed by the unit and hencesuch working fluid will pass inwardly through the rotating ring ofliquid and will collect in the descending pockets or working chambers 72at the left-hand side of the rotor, Figure 1. At this time, the ballvalves 74 are seated on the inner ends of the fluid passageways 73,serving as check valves between each pumping chamber and thedischargepressure within thecenter of the easing. The working fluidfills each chamber 72 and passageway 73 in the downward rotationthereof, and as each pocket approaches the bottom of the rotor, theapproachinglevel of the inner leg as contacts with the outer edge of thedividing wall 69 at the rear ofthe chamber, thereby sealing the workingfluid therein. The diminishing radius of the intermediatedisplacementmember 79 tends to force the intermediate leg of the liquid ring intothe working chambers, thereby compressing the trapped fluid therein.

The decreasing radii of thetwo outer displacement members 81 also coacton the outer legs y to produce the desired differential or unbalancebetween the intermediate and outer legs for obtaining the compressionpressure. The volume of liquid displaced from the channel area 68 by thedecreasing radius of the intermediate displacement member 7 9 augmentsthe quantity of liquid available in the outer legs 2 for producing alarge differential between the legs during the compressionstage.Attention is also directed to the fact that the pressure at which theworking fluid is discharged from the; device is effective on the outerlegs 3 during this compression stage'of the cycle. When the pressurein'each working chamber reaches the desired 'efxhaust pressure, the ballvalve 74L is forced from its seat and the working fluid is dischargedinto the central space within the casing, from whence it is conducted toits point of use throughthe outlet connection 39.

It will be seen that by virtue of having the side flangesGl, 64 projectoutwardly beyond the outer edges of the dividing walls 69 the admissionofthe working fluid can be made to occur directly into the peripheralchannel 68 of the rotor through a stationary inlet duct 85 projectinginto this channel. The peripheral edges of said flanges 64, 64 areindicated in dotted lines in Figure 1 and it will be seen that theseflanges prevent the working fluid which is being admitted through theport 85 from bubbling across or around the edges of the rotor at theintake 'zone,-the exhaust pressure eflective on the outer legs 3 alsoaiding in preventing this.

When the inner'leg w passes the offset portion 83 it is thrown outwardlyfrom each chamber by centrifugal and tangential force, thus creating ararefied condition in that chamber which aids in effecting a quickadmission of the working fluid thereto. The admission of the workingfluid directly into the peripheral channel of the rotor enables theentire interior of the casing, within the rotating liquidpumping ring,to be used as an exhaust chamber for all the working chambers.

It will be understood that the radius of the rotor and the shape andproportions of the three displacement members 7 9, 81 and 81 may bechanged for obtaining any desired dlfi'erential between the inner andouter legs will be understood that at the intake stage,

these lateral displacement members are of lesser depth even than theportions illusused for different pressures.

The use of mercury is typical, permit-ting the attainment of relativelyhigh pressures in a unit of small radius, such pumping liquid also beingsubstantially inert in most instances to chemical reaction with theworking fluid being pumped.

In using mercury, the metallic construc tion of the device would, ofcourse, be such as not'to va'malgamate with the mercury. Obviously,water or any of the other liquids of lower or higher specific gravitiesmay be used as the pumping liquid. Liquids of high specific gravities,which might be used, are represented by acetylene tetrabromide, leadchloride, lead bromide and bismuth bromide. In Figures 3 and 4 I haveillustrated other embodiments wherein one valve function utilizes aliquid ring which is contained entirely within the rotor.- This valvefunction may be either for the inlet oroutlet of the working chambers,but is preferably for the outlet discharge from these working chain'-bers, and possesses the advantage of affording a liquid seal whereby theworking fluid, discharged from the working chambers, can be conductedfrom the hollow interior of the rotor to a point outside of the mainpump casing without having to pass through a gland packing or otherrotating joint such as might be susceptible to leakage.

I Referring to the construction shown in Figure 3, and wherein partssimilar to parts of Figures 1 and 2 have been given the same referencenumerals with the appendix 9, the rotor has the previously describedarrangement of peripheral pumping chambers 72 which are preferablyarranged to emerge from the pumping ring of liquid 00, y to haveadmission occur across the periphery of the rotor, although it will beunderstood that admission may be arranged to occur in accordanoe withthe method employed in the embodiment of Figures 1 and 2. Instead ofemploying displacement members to cause the pumping ring to exertpumping impulses in the rotor chambers, I have, in this embodiment,shown the rotor 52 as being eccentrically disposed in the housing.Hence, the rotor is caused to dip into the rotating ring of pumpingliquid at the near side of the housing, which is preferably the bottom,and in thus dipping into the liquid a certain amount thereof isdisplaced to establish the prepon derating outer legs 3 3 in the pumpingring. At the upper side of the housing the rotor emerges from thepumping ring for permitting the intake of the working fluid across theperiphery of the rotor and into the pumping chambers. That is to say,the quantity of liquid making up the liquid pumping ring is soproportioned with reference to the volumetric displacement of the rotor,the degree of its eccentricity in the housing, etc., that at the intakestage of the cycle the liquid pumping ring separates completely from theperipheral edges of the rotor, so that the working fluid can enter thepumping chambers around such peripheral edges.

It will be seen that the construction shown in Figure 3 has in commonwith the construction shown in Figures land 2 the admission of theworking fluid peripherally to the working chambers, i. e., in each ofthese embodiments the working fluid is introduced into the workingchambers at the periphery of the rotor. The peripheral admission inFigure 3 differs from that of Figures 1 and 2 in that it occurs from thesides of the rotor across the edgesof the channel flanges instead offrom an inlet duct extending into the rotor channel. It will also benoted that in the construction shown in Figure 3, the

easing enclosure or area within. the *liquid pumpingring is at admissionpressure, whereasin Figures 1 and 2 this area is at exhaust pressure,being sealed off. from the peripheral channel by the side legs; of theliquid pumping ring. In Figure 3 the working fluid is admitted to theinterior ofthe housing through the inlet, connection 36 opening into theside thereof. e

The driving shaft 42 is rigidly secured to one of the side plates 64 ofthe rotor, such being shown as theright-hand plate.

Any suitable couplingmeans, generally indicated at 121, may be employedfor connecting this shaft to the plate in driving relation, thiscoupling means sealing the joint between the shaft and plate to preventleakage from the interior of the rotor outwardly along the shaft. Theleft-hand side plate 64 of the rotor has a central opening 122 thereinthrough which liquid is automatically supplied from the main pumpingring a7, y to the interior of the rotor for replenishingthe sealing.ring and inner valve ring, which I shall presently: describe. Extendinginwardly from each working chamber 72 is a discharge tube 96 thedischarge. end of which is doubled, back to face in: an outwarddirection. vliev'olving with the rotor, inside thereof, is the valvering of liquid .2. C0- operating with the discharge end of each tube 96is a valve cup 124 which is partly immersed inthe valve ring 2'. Each ofthese valve cups preferably has a washer 125 of rubber or like pliablematerial in the bottom thereof in'order more effectively to seal thedischarge end of the tube, 96 when'the valve cup is pressed in an inwarddirection against such discharge end. It will be evident that thepressure established in the liquid valve ring 2 by centrifugal force,will normally tend to force the'valve cup in an inward direction againstthe. discharge end of the tube when the rotor is revolving.

The discharge pressure of the working fluid, which may be relativelyhigh, prevails within the interior of the'rotor, and, this pressureacting on the valve ring 2" also tends to' ring a and in the valve cupsgo up together and hence variations of speed do not appreciably aflectthe valve function. The annular flange portion of each cup is spacedfrom the outer wall of the tube to permit ready egress of the workingfluid when the valve is unseated and any suitable guide stem or likeguide means 127 may be provided for retaining-the valve cups inoperative alignment with the discharge ends of said tubes. When theworking fluid in'each working chamber is placed under pressure in thebottom part of the rotation of the rotor,-.'this pressure forces thevalve cup 12 away from the discharge end of the tube 96 in an outwarddirection in the ring of liquid a, substantially as illustrated of thelower valve cup in Figure 3., The hollow interior of the rotor forms amanifoldarea 129f-into which allof the working'chambers, discharge inthis same manner as they revolve down through the bottom of the rotorcycle.

Such 'nside manifold area-is sealed at left-hand side of the rotor by'adisk 131 which is spaced inwardly slightly from the adjacent side plate64 of the rotor. The periphery of this diskis also spaced slightly from.the drum portion defining the bottoms of the working chambers. A sealingring of liquidz rotates in the annular'space between the disk 131 andthe adj acentside plate 64;, thisring of liquid sealing the interiormanifold area 129 from communication with the interior of the housing,outside of the rotor; 1 I

The inner leg of this annular liquid seal is subjected to the dischargepressure prevailing in the manifold area 129 and the outer leg is onlysubjected to'the admission pressure prevailing in the interior of thehousing, and hence the latter leg will have to extend inwardly towardthe center of the rotor toa greater distance to balance the pres.-sureleg. If desired, a ring 132 may be dis posed as a spacer betweentheinner leg of this sealing ring 2'- and. the body of liquid forming thevalve controlling ring a. i

The. disk 131 may be arranged for rotatio with the rotor, in which caseit would be connectedtherewith bysuitable bridge or spider members, orsuchdisk may beheldstation'ary within the rotor, the latter practicebeing preferable. Said disk is secured to the flanged end of a tube 134extending out through the side wall of the housing,-the disk-having acentralopening therein communioating with the bore of the tube.v

The working fluid under pressure is dis chargedvfrom the device throughthis tube 134;. When the disk is to rotate with the -rotor, such tube isrotatably mounted in the 1 bearing 135' which is secured to the sidewall of thehousing, and when such disk is to remain stationarythistubeis rigidly secured in said'bearing.v a

When the rotor is started, the sealing and valvecont'rolling rings ofliquid 2" and-z are brought to theproper levels and are maintained atthese levels through an automatic replenishing and overflow actionutilizing a tube 137 which is secured, as by a bracket 138, to theleft-hand wall of thehousing. I

The outer inlet end of this tube extends into the ring of pumping liquidand has'its end bent to dispose the opening of the tube the valvecontrolling ring .2, are both maintained substantially at the samelevel.

If this level should be too low or recede oecause of insufiicientliquid, the preponderating outer leg of the sealing ring willimmediately replenish these inner bodies of liquid, being in turnreplenished through the tube 137, and if this inner sealing leg andvalve controlling ring should have an excessive amountof liquidproducing an objectionably high level, the discharge pressure of theworking fluid acting thereon will cause such excess liquid to be forcedback into the outer leg of the sealing ring for spilling over throughthe opening 122 back into the pumping ring.

InFigure 4: the pumping ring of liquid at, 3/ is given its pumpingimpulses through the action of the displacement members 79 81although'it will be evident that these pumping impulses may be obtainedby disposing the rotor eccentrically in the housing as is shown inFigure 3. The intake occurs transversely across the periphery of therotor, but, here again, the intake may be arranged to occur inaccordance with any of the previously described embodiments. The,discharge tubes 96 extend inwardly towards the center of the rotor to agreater distance than in Figure 3, and have their outlet valve functioncontrolled directly by the valve ring of liquid 2. 7

The ends of the discharge tubes are im mersed only slightly in thisvalve ring, so that when the working chamber associated with one of thetubes is in its pumping or compression cycle the working fluid canreadily blow over or out through the end of the discharge tube and upthrough the ring of pumping liquid, into the interior of the r0- tor.When such working chamber is moving'through the intake stage of itscycle a portion of the liquid rin'g is sucked into't-he end of thedischarge tube, substantially as illustrated at the upper part of Figure4. The centrifugal force of this liquid leg pro; vents the liquid frombeing carried over into the working chamber, and the volume of liquid inthe ring 2 is such that the relatively small quantity of liquid suckedinto'such discharge tubes does not materially lower the level of thevalve ring.

The liquid sealingring a is illustrated as being of greater depth and ofgreater diameter. That is to say, the adjacent wall of the workingchambers is extended outwardly beyond said working chambers in the formof an annular plate 139, which is secured to the outer, left-hand rotorplate 64 as by providing both of these plates with laterally extendingflanges, and securing the same together over the disk 131. This disk 131may rotate or may be held stationary. It is preferably held stationary,and has a liquid replenishing or supply tube 142 secured to the upperportion thereof by a bracket 143.

The valve ring of liquid 2 is at a diflerent level than the inner'leg ofthe sealing ring .2 and the tube 14.2 has its inlet end facing counterto the direction of rotation of the sealing ring so that liquid iscontinuously supplied through said tube to the valve ring a, theoverflow from such latter ring spilling over the wall 132 back into thesealing ring. This sealing ring is continuously replenished from theliquid pumping ring through the tube 137 substantially as described ofFigure 3, the overflow from this sealing ring spilling through theopening 122 back into the pumping ring. The manner in which the workingfluid is conducted into the housing through the inlet connection 36 ispumped or compressed in the working chambers, and is discharged throughthe outlet connection 134:,

will be apparent from the preceding descripopens into the housing on oneside of the rotor,

and the outlet connection 39 opens into the housing on the other side ofthe rotor.

One of the side plates or flanges 64 of the rotor is of sufiicientdiameter to accommodate the necessary difference of levels on oppositesides thereof for sealing the intake side from the outletside, thepumping ring of liquid also serving as a sealing ring in cooperationwith this flange or plate.

I The working fluid is admitted to the working chambers through tubes145, there being one of these tubes for each chamber extending throughthe'inner or top wall of the chamber edge of each dividing wall 69separating the working chambers, so that when the pumping ring has madecontact with the two end walls 69 of a particular working chamber forsealing the bottom of the chamber the pumping ring has also contactedwith the outer end of the tube 145 so that such tube is sealed againstegress of the working fluid. 'It will be evident thatas the: pumpingring surges inwardly into the working chamber and builds up its pressuretherein suchpressure merely causes the liquid of the pumping ring toflow inwardly to a greater extent in the tube 145. The centrifugal forceof the leg of liquid in-this tube maintains the tube closed w andperforms the valve function.

If desired, the outer end ofeach tube 145 may terminate at a shorterradius. so that the device can be designedor the pumping ringproportioned whereby such ring will never separate from contact with theouter edges of the transverse dividing walls 69 but will always remainin sealing engagement with these walls for maintaining a constantliquidseal between adjacent working chambers. In either construction, when theworkingchamber revolves into the intake stage of itscycle the pumpingring recedes out of contact with the outer end of the tube 145, therebyopening said tube to the admission of the working fluid through theinner end thereof and into the working chamber.

The discharge occurs; through passageways 96 extending from the workingchambers andopening outwardly through the opposite face or side of therotor. In. this instance. the valve function is shownas being'performedby a continuous ring' member 147 which is mounted on the side of therotor to overlie the outlet ends of all of these passageways. Thisannular valve member has its inner peripheral edge seating on an annularshoulder 14-8, and is retained in position by an outer ring 149 whichoverlies the inner edge of the valve ring member 147, such retainingring 149 being secured to the rotor by screws or'in, any other suitablemanner.

The valve member 147 may have a slight amount of lateral play bet-weenthe rotor and the retaining ring 149. Such valve ring 147 preferablyconsists of a very thin metallic ring, of only a few thousandths of'aninch thickness. Where the workingchambers are moving through the intakestage of their cycle, this ring will beheld pressed tight against theends of the discharge passageways 96 by the difference of pressuresbetween such chambers and the discharge chamber area to the left of therotor. Where the working chambers are moving through the pumping orcompression stage of their cycle, this ring will flex away from theoutlet ends of said passageways under the pressure of the working fluidbeing discharged through said passageways. Such fiexure will be in theform of a wave motion inthe ring. It will be noted that such form ofvalve means is not influenced by centrifugal force 1101' variations inthe rotor speed. This formof outlet valve means maybe employed withdifferent forms of rotors having difierent intake valve functions. Forexample, suchoutlet valve, means maybe employed in embodiments whereinthe intake of the workingfluidoccurstransversely across the. peripheryof the rotor at one side thereof, as illustrated in Figure 4. This alsoapplies to the other embodiments previously described, the inlet valvefunctions or rotor and the casing, and without having to resort to'movable abutments, rotating metallic pistons, etc. Hence, there are noparts to wear or to require lubrication or replacement, and leakage ispractically eliminated.

The avoidance of lubrication and leakage particularly adapt thisconstruction to use as a compressor for handling refrigerant in domesticor commercial refrigerating apparatus; but, it will, of course, beunderstood that the construction is also adaptable to use as an air orgas compressor, and can also be used for pumping liquids. 'In one" use:as a liquid pump, the rotating liquid pumping ring 00, y, 1 would beofhigher specific gravity than the liquid being pumped. In another useof the device as a liquid pump, the liquid being circulated through thedevice could function as its own liquid pumping ring w, y, 'y. In thisregard, when used as a refrigerant compressor, some of the refrigerantin the liquid state could beused as the pumping ring, which would becontinuously replenished by the entering refrigerant.

Aside from its use as a pump or'compressor, there are numerous featuresof my construction which can be, adapted to rotary internal combustionengines, and I have phrased some of the appended claims to cover suchpossible adaptations.

While the general construction which I have disclosed constitutes one ofthe preferred embodiments of the invention, nevertheless, it willbeunderstood that such is merely exemplary and that numerousmodificationsand rearrangements may be made without departing from theessence and broad scope of the invention. 5

I claim: i

1. In a .device of the class described, the combination of acasing, arotor therein having two laterally spaced annular flanges projectingtherefromto form a peripheral channel in the rotor, an inlet and anoutlet for the pumped fluid, means defining working chambers in saidchannel, separate. working fluid passageways in said rotor communicatingwitheach of said chambers, a liquid adapted to be revolved within saidcasing by said rotor and producing under the action of centrifugal forcea liquid ring having piston coaction with said working chambers, and adisplacement member extending into the peripheral channel between saidflanges for causing piston surging of the liquid ring in said channel 2.In a device of the class described, the combination of a casing, a rotortherein having two laterally spaced annular flanges projecting therefromto form a peripheral channel in the rotor, an inlet and an outlet forthe pumped fluid, means defining working chambers in said channel,separate working fluid passageways in said rotor communicating with eachof said chambers, a liquid adapted to be revolved within said casing bysaid rotor and producing under the action of centrifugal force a liquidring having piston coaction with'said working chambers, said liquid ringin one part of the rotor cycle forming an inner liquid leg within theperipheral channel of said rotor and outer liquid legs on the outersides of said rotor acting in centrifugal pressure opposition to saidinner leg, and displacement means on the outer sides of said rotor forincreasing the radial depth of said outer legs relative to the radialdepth of the inner leg. 7

3. In a device of the class described, the combination of a casinghaving an inlet and an outlet for the pumped fluids, a rotor thereinhaving two laterally spaced annular flanges projecting therefrom to forma poripheral channel in the rotor, means defining workin chambers insaid channel, separate 1 working fluid passageways in said rotorcommunicating with each of said chambers, a liquid adapt-ed to berevolved within said casing by said rotor and producing under the actionof centrifugal force a liquid ring having piston coaction with saidworking chambers, said liquid ring in one part of the rotor cycle,formingan inner liquid leg within the peripheral channel of said rotorand outer liquid legs on the outer sides of said rotor acting incentrifugal pressure opposition to said inner leg, a displacement memberrelatively to which said rotor revolves and extending into theperipheral channel between said flanges for causng piston surging of theinner leg of said liquid ring, and displace ment means disposed on theouter sldes of said rotor for increasing the radial depths of said outerlegs relatively to the radial depth of the inner leg to produce acentrifugal pressure differential between said outer and injectingtherefrom to form a peripheral channel in the rotor, means definingworking chambers in said channel, separate working fluid passageways insaid rotor communicating with each of said chambers, a liquid adapted tobe revolved within said casing by said rotor and producing under theaction of centrifugal force a liquid ring having piston coaction withsaid working'chambers, and a stationary displacement member in saidcasing having an inner surface of gradually de creasing radius extendinginto the peripheral channel between said flanges for causing an inwardcompression surging of the liquid ing with each of said chambers, aliquid adapted to be revolved within said casing by said rotor andproducing under the action of centrifugal force a liquid ring havingpiston coaction with said working chambers, said liquid ring in one partof the rotor cycle forming an inner liquid leg within the pe ripheralchannel of said rotor, and also forming two outer liquid legs on theouter sides of said-rotor acting in centrifugal pressure opposition tosaid inner leg, and stationary displacement surfaces of graduallydecreasing radius disposed on the inner and outer sides of the saidperipheral channel for creating a centrifugal pressure differentialbetween said outer and inner legs in the compression stage of the rotorcycle.

6. In a device of the class described, the combination of a casinghaving an inlet and an outlet for the working fluid,a rotor thereinhaving two laterally spaced annular flanges projecting therefrom to forma peripheral channel in the rotor, means defining working chambers insaid channel, separate working fluid passageways in said rotorcommunicating with each of said chambers, a liquid adapted to berevolved within said casing by said rotor and producing under the actionof centrifugal force a liquid ring having piston coaction with saidworking chambers,

and liquid governed centrifuge-11y acting,

valve means controlling said working fluid passageways.

7. In a device of the class described, the combination of a casing,having an inlet and an outlet for the working fluid, a rotor thereinhaving two laterally spaced annular flanges projecting therefrom to forma peripheral channel in the rotor, means defining working chambers insaid channel, separate working fluid passageways in said rotorcommunicating with each of said chambers, a liquid ton coaction withsaid working chambers,

and valves normally lhBld closed by the centrifugal force of a liquidring arranged for controlling said working fluid passageways.

8. In adeviceof the class described, the combination of a casing, arotor therein havingtwo laterally spaced annular flanges projectingtherefrom to form a peripheral channel in the rotor, means definingworking chambers in said channel, separate working fluid passageways insaid rotor communicating with each of said chambers, a liquid adapted tobe revolved within said casing by said rotor-and producing under theaction of centrifugal force a liquid ring having piston coaction withsaid working chambers, a displacement member extending into the periph-'eral channel betweensaid flanges for causing 7 piston surging of theliquid ring insaid channel, a working fluid inlet port opening into saidchannel through said displacement memher, and an outlet from said casingfor the working fluid.

9. In a device of the class described, the combination of a casinghaving an inlet and an outlet for the working fluid, a rotor thereinhaving two laterally spaced annular flanges projecting therefrom to forma peripheral channel in the rotor, means defining working chambers insaid channel, separate working fluid passageways in said rotorcommunicating with each of said chambers, aliquid adaptedtobe revolvedwithin said casing by said .rotor and producing under the action ofcentrifugal force a liquid ring having piston coaction with said workingchambers, liquidsealing means in said rotor controlling the flow ofworking fluid through said passageways, and means automaticallygoverning the height of said liquid sealing means.

10. In a device of the class described, the combination of a casinghaving an inlet and an outlet for the working fluid, a rotor thereinhaving two laterally spaced annular flanges projecting therefrom to forma peripheral channel in-the rotor, means defining working chambers insaid channel, separate working fluid passageways in said rotorcommunicating with each of said chambers, a liquid adapted to berevolved within said casing by said rotor and producing under the actionof centrifugal force a liquid ring having piston coaction with saidworking chambers, liquid valve means comprising a rotating ring ofliquid in said rotor for controlling the flow of workingfluid throughsaid passageways, and means automatically governing the depth of saidlatter liquid ring in rotation.

11. In a device of the class described, the combination of a casinghaving an inlet and an outlet for the working fluid, a rotor thereinhaving two laterally spaced annular flanges projecting therefrom to forma pcripheralchannel in'the rotor, means defining working chambers insaid channel,'separate working fluid passageways in said'rotorcommunicating at one end with each of said chambers, a liquid adapted tobe revolved within said casingby said rotor and producing under theaction of centrifugal force a liquid ring havingpiston coaction withsaid working chambers, the other ends of said working fluid passagewaysrotating in 00- operating relation to a rotating liquid ring, and valvemeans cooperating with said latter llquid ring for sealing the latterends of said passageways.

'12. In a device of the class described, the V combination .of a casinghaving an inlet and an ,outletfor the working fluid, arotor thereinhaving two laterally spaced annular flanges projecting therefrom to forma peripheral channel in the rotor, means defining working chambers .insaid channel, separate working fluid passageways in said rotorcommunicating with each of said chambers, a liquid adapted to berevolved within said casing by said rotor and producing under the actionof centrifugal force a liquid ring having piston coaction with saidworking chambers, a series of rotating discharge ports connecting withsaid working fluid passageways and cooperating with another rotatingliquid ring, and means for displacing liquid from said first liquid ringto replenish the supply of liquid insaid other liquid ring.

13. In a device of the class described, the combination of a casinghaving an inlet and an outlet for the working fluid, a rotor therein,dividing walls extendin transversely of the periphery of the rotor i ordividing said periphery into a plurality of working chambers,-twolaterally spaced annular flanges on said rotor and extending outwardlytherefrom beyond said dividing walls to form a pcri-pheral rotor channelin the plane of said working chambers of greater depth than said workingchambers, .a liquid adapted to be revolved within said casing andproducing under the action of centrifugal force a liquid ring havingpiston coaction with said working chambers, and means for controllin thedischarge of working fluid from said c ambers comprising a liquid ringrevolving'in said rotor.

.14.;1113 device of the class described, the combination of a casing, arotor therein, means definlinga plurality of working chambers inthe'perip'hery of said rotor, working fluid passagewaysfni said rotorcommunicating with said chambers, a liquid valve ring in said rotorcontrolling one of said working Lfluid passageways, means for supplyingthe \working .fiuid to the interior of said casing, "an outlet for theworking fluid, a

centrifugal force a liquid ring coacting with said rotor, and means forcausing said liquid ring to exert pumping impulses in said workingchambers and to recede from said working chambers for permitting theworking fluid to enter said chambers peripherally of the rotor from theinterior of said 1 casing.

' ing chambers, means for admitting the working fluid into the interiorof said casing, means for conducting the exhaust working fluid from theinterior of said rotor, and liquid sealing means separating the interiorof said casing from the interior of said rotor.

16. In a device of the class described, the combination of a stationarycasing, a'rotor therein having a plurality of working chambers formedsubstantially in the periphery ofsaid rotor, an inlet and an outlet forthe working fluid, the sides of said rotor being spaced from the sidesof said stationary casing, a liquid adapted to be revolved within saidcasing approximately at the speed of said rotor and producing under theaction of centrifugal force a liquid ring having piston coaction withsaid working chambers, said liquid ring being adapted to extend into thelateral spaces between the sides of said rotor and the sides of saidstationary casing for sealing said rotor, and a coacting liquid sealingring revolving within said rotor.

17. In a device of the class described, the combination of a casing, arotor therein, an inlet and an outlet for the working fluid, meansdefining a working chamber in said rotor, a liquid ring revolving withinsaid casing, exteriorly of said rotor, a second liquid ring revolvinginside of said rotor, one of said liquid rings exerting pumping impulsesin said working chamber, and a valve passageway leading from saidworking chamher and cooperating with the other liquid ring.

18. In a device of the class described, the combination of a casing, arotor therein, an inlet and an outlet forthe pumped fluid means defininga working chamber in said rotor, a liquid ring revolving within saidcasing exteriorly of said rotor and creating pumping impulses in saidworking chamber, a valve passageway communicating between said workingchamber and the interior of said rotor, a closure member, and a liquidring revolving inside of said rotor and cooperating with said closuremember for casing and producing under the action of creating pumpingimpulses in said working chamber, and a working fluid passageway insaid'rotor havin a port communicating with said working chamber at apoint where saidport will be immersed and sealed by said liquid ringsubstantially in the initiation of the pumping impulse in the workingchamber.

20. In a device of the class described, the combination of a casing, arotor therein, an inlet and an outlet for the working fluid, meansdefining a plurality of working chambers in said rotor, a liquid ringrevolving within said casing and creating pumping impulses in saidworking chambers, discharge passageways leading from said workingchambers and discharging from one side of said rotor, and a relativelythin flexible valve member-carried by the rotor and adapted to close thedischarge ends of said passageways, said valve member flexing away fromthe ends of said passageways when the working fluid is dischargedtherethrough and being disposed substantially radially of the rotor soas to remain substantially uninfluenced by variations of centrifugalforce.

21. In a device of the class described, the combination of a casinghaving an inlet and an outlet for the working fluid, a rotor in saidcasing, means defining a plurality of working chambers in said rotor, aliquid ring revolving within said casing and creating pumping impulsesin said working chambers, discharge passageways in said rotor leadingfrom said working chambers, and valve means for said discharge passagescarried by said rotor and arranged whereby the functioning of said valvemeans and the pressure required to open said passages remainuninfluenced and substantially constant during any variations ofcentrifugal force resulting from different rotor speeds.

In witness whereof, I hereunto subscribe my name this 25th day ofJanuary, 1930.

WILLIAM P. DALRYMPLE.

